Roll-over actuator for two-way plow



March 22, 1960 R. CHANDLER ETA!- ROLL-OVER ACTUATOR FOR TWO-WAY PLOW Original Filed April 19. 1954 2 Sheets-Sheet l k INVENTORS. W/"MNN 8 McMAN/G'AL Af/arm s for A a 011E401 ROY L. CH

March 22, 1960 R. L. CHANDLER EI'AL ROLL-OVER ACTUATOR FOR TWO-WAY PLOW 2 Sheets-Sheet 2 Original Filed April 19. 1954 NDL ER ROY L, CHA

CLAUDE a 0625, m,

INVENTORS. WHANN 8 McMAN/GAL Af/OI'MS 9! A gal/cam 2,929,456 ROLL-OVER ACTUATOR FOR TWO-WAY PLOW Roy, L. Chandler, Hurst, Tex., and Claude B. Ogle, Jr.,

Pasadena, Qalifi, assignors to Atlas Scraper and Engineering (10., Bell, Calif.

Original application April 19, 1954, Serial No. 424,108, now Patent No. 2,830,519, dated April 15, 1958. Divided and this application February 17, 1958, Serial No. 715,628

8 Claims. (Cl. 172-226) 424,108, filed April 19, 1954, now Patent No. 2,830,519,

granted April 15, 1958.

It is one object of the herein describedinvention to provide improved means in a two-way plowfor actuat-- ing the roll-over frame, wherein it becomes unnecessary to provide latching means for retaining the rollover frame against roll-back, thus enabling the plow bottoms to heel over slightly for quick penetration upon starting the plowing operation, yet prevent roll-back of the rollover frame while plowing; which provides a,variable transmission; and which also acts to actuate a power operating means with retarding effect.

Another object is to provide in a two-way plow having plow bottoms on an offset roll-over framestructure, unique means for actuating the roll-over frame,-wherein a greater mechanical advantage is obtained at the start of the rolling action to overcome the inertia and unbalanced load of the offset structure and in, which the mechanical advantage decreasesthrough the mid-portions of the rolling'action where the load is more .nearly balanced, and in which greater mechanical advantage 'isv again obtained during the final portion ofthe rolling action, thus making it possible to accomplish the rolling action with minimum power, free of finalimpact, and without the necessity of having to resort to theuseof expensive and complicated counterweights or spring arrangements. t L

Further objects of the invention will be brought out in the following part of the specification; wherein detailed description is for the purpose of fully disclosing the invention without placing limitations thereon. a

Referring to the accompanying drawings, which are for illustrative purposes only: t

Fig. 1 is a side elevational view of a two-way plow embodying the features of the present invention;

Fig. 2 is an enlarged fragmentary perspective view showing details of the power actuating devices and associated parts for operating the plow;

. Fig. 3 is an enlarged side elevational fragmentary view showing the details of the plowing depth gauging wheel; as viewed along the line 33 of Fig. 4;

Fig. 4 is a plan view of the plow shown in Fig. I;

Fig. 5 is an enlarged fragmentary perspective view illustrating the details of the power actuating means for turning the roll-over frame for selectively bringing the plowing elements into operative position; and

Fig. 6 is an enlarged fragmentary sectional-view showing parts of the power transmitting means for turning the roll-over frame, taken substantially on line 6-6 of Referring more specifically to the drawings, the plow 2,929,455 Patented Mar. 22, 1960 assembly is arranged to be towed behind a powered vehicle such as a tractor. In general, the plow assembly includes'a mobile carrier frame 10 supported upon wheels 11 and 12. Extending rearwardly of the carrier frame 10 is a roll-over frame 13 which carries a left-hand plow gang 14 and a right-hand plow gang 15. The rearmost end of the plow assembly is provided with a caster wheel 16 which cooperates with the wheels 11 and 12 to form a three point support for the plows, and are also utilized for controlling the plow operations as well as for transporting the plow from one location to another.

Considering the plow assembly more specifically, the carrier frame comprises a transversely extending box frame 17, as shown in Figs. 1 and 4, having end members 20 and 21, and a top plate 22.

A plurality of forwardly extending bracket members 23, 24, 25 and 26 are secured at their rear-ends to the box frame 17in spaced apart relation, and at their outermost ends form bearing supports for a rotatable shaft or axle structure 27. This shaft structure at its opposite ends is provided with a projecting arm 28 in each case which supports the wheel 11 or wheel 12 for rotation about: an axis offset with respect to the shaft structure 27..

A tongue structure 29 includes rearwardly diverging side rails 30 and 31, the side rail 39 being pivoted at its rear-end on the shaft structure 27 between bracket members 23 and 24, while the side rail 31 is pivoted at its rear-end on the shaft structure 27 between the bracket members 25 and 26. The tongue is thus supported for vertical swinging movements about its rear-end by suitable power means. 1

More specifically, the power means comprises a power liftingdevice whichmay be a single cable operable, by thetractor, or. as disclosed in the present case a fluid cylinder 32 having a pivoted anchor connection 33 at one end with the tongue 29. A power delivery element 34 is operatively associated with the fluid cylinde'r and connected with the shaft structure 27 through a lost motion connection. t

. As 1 most clearly shown inv Fig. 2, the lost motion-connection comprises a coupler 35 fabricated from plate members which are welded or otherwise secured together to form a projecting arm structure rotatable with the shaft structure. ,.As .shown, the coupler includes a back plate 36,.a front plate 37 and side plates 38 and 39 which cooperate in assembled relation to form in effect a socket 49. .A. fioatinglink 41 is arranged with oneend positionedwithin the socket 40, this end being pivoted on a pivot pin lzsup'ported by the sideplates 38 and, thusenabling limited angular movement of the link 41 between the back plate 36 and front plate 37. The free end of the floating link 41 is connected with the power delivery element 34-.

.Movement of the. coupler 35 in a clockwise direction for raising the rear-end of the tongue with respect to the wheels 11 and 12 is limited by an abutment stop member 43 on the tongue structure. Movement of the coupler 35 in an opposite direction is normally limited by engagement of a projection,(not shown) on the side plate 38 with one end of an abutment screw 45 which is longitudinally adjustable within a support 46 mounted on the box frame 17 of the carrier frame, lock nuts 47 being provided for retaining the abutment screw in adjusted position. The abutment screw is utilized for determining the plowing depth.

The carrier frame in its broad concept is susceptible of use with various types of earth working tools, but for purposes of illustration has been disclosed herein as being associated withthe, left-hand, gang and right-hand gang of a two-way plow arrangement. The plow gangs are shown primarily in Fig. 4 as being supported on the rollover frame 13 which embodies-a triangular box-like platform 48 which is secured along one edge to a tubular member 49 rotatably supported upon a hollow stationary tube 50 for roll-over movement about the longitudinal axis of the tube. The tube is supported at one end Within a tubular sleeve forming a part of the box frame 17 and secured thereto by welding or other conventional means. The tubular sleeve is positioned centrally between the wheels 11 and 12, and so that the stationary tube 50 will project rearwardly and be in axial alignment with the longitudinal axis of the tongue 29. The tube 50 is fixedly secured by a securing bolt 52 passing through aligned openings in the tubular sleeve and tube 50. Thus, the tube 50 is removably mounted in the sleeve.

in the plow assembly as shown in Fig. l the roll-over frame 13 is retained against axial movement on the stationary tube 56 by a thrust sleeve 53 at the rearend of the tube 58, the thrust sleeve and tubular member 49 having cooperatively associated thrust flanges 54 and 55. i

Associated with this end of the plow assembly, there is provided a swingably mounted bearing bracket 56, this bracket being pivoted for vertical swinging movemeut about a pivot pin 57 which also functions to secure the thrust sleeve 53 to the associated end of the stationary tube 50. This bracket has mounted therewith a bearing 58 which rotatably supports a fork 59 on which the caster wheel 16 is mounted. At the upper end of the fork 59 is a disc 60 which is provided with a dwell point 61 in its periphery for receiving a spring actuated detent roller 62 therein, when the caster wheel is in a trailing position. This detent tends to stabilize the caster wheel and prevent flutter when trailing.

The rear-end of the plow assembly is thus arranged so that it may be raised and lowered with respect to the caster wheel 16, by swinging the bearing bracket 56 about the pivot pin 57 by means of a suitable actuator. For such purpose, there is provided a second fluid cylinder 62 which is anchored at one end to a lug 63 carried by the thrust sleeve 53. The fluid cylinder has operatively associatedwith it a power delivering element 64 having its outer end pivotally connected to a projecting arm 65 of the bearing bracket 56. With the power delivery element fully extended, the associated end of the plow assembly will be raised with respect to the caster wheel 16, and with the power delivery element 64 retracted, the associated end of the power assembly will be in a lowered position with respect to the caster wheel.

As clearly shown in Fig. 4, a plow gang, in this instance the right-hand gang, comprises four individual plow elements or bottoms which are secured to the rollover frame so that the gang as a unit is ofiset with respect to the turning axis of the roll-over frame. With the ofiset arrangement, it will be observed that the innermost plow bottom is directly below the turning axis, when the gang is in operating position, and that the outermost plow bottom is positioned at least a distance from the roll-over axis as great as the path of movement of the wheel 12. By offsetting the plow gangs in this manner, and with the turning axis of the roll-over frame aligned with the mid-axis between the wheels 11 and 12, and the longitudinal axis of the tongue 29, the tractor and wheels 11 and 12 as well as a depth gauging wheel 66 are all permitted to run on unplowed ground. A definite reference plane is thus established for the plowing operation, and it is not necessary to provide horizontal tongue shifting devices as in many of the conventional arrangements in plows of this type, where one of the wheels for the carrier frame must operate in a previously plowed furrow.

Heretofore, it has been the customary practice to mount the plow gang as nearly symmetrically as possible with reference to the turning axis of the roll-over frame, in order that the size of the power actuating means for sector gear- 67.

turning the roll-over frame might be kept within practical limits of size. Utilization of an off-set plow gang sufficiently to permit running on unplowed ground is made practical by utilization of unique means for actuating the roll-over frame, wherein a greater mechanical advantage is obtained at the start of the rolling action to overcome the inertia and unbalanced load of the offset structure, and in which the mechanical advantage decreases through the mid-portion of the rolling action where the load is more nearly balanced, the greater mechanical advantage again coming into play during the final portion of the rolling action. With such an arrangement, it is possible to accomplish the rolling action with minimum power, free of final impact, and without the necessity of having to resort to the use of expensive and complicated counterweights, springs, etc.

As shown in Figs. 5 and 6, the tubular member 49 is fitted adjacent its forward end with a sector pin gear 67 having operative relationship with a driving member 68.

The driving member 68 comprises a fiat plate 69 which is secured to a turning bracket 70 supported at one end in a bearing 71' on the box frame 17. The outer edge of the plate 69 isprovided with spaced indentations 71 which extend generally in a radial direction from the rotational axis of the plate 69 and open outwardly for 7 driving cooperation with pin supported rollers 72 in spaced apart relation adjacent the peripheral edge of the The spacing between the indentations '71 defines spaced projection lobes 73 adapted to successively extend between the rollers 72 during driving operation. These lobes are effective to restrain movement of the roll-over frame by virtue of its center of gravity being offset with reference to its turning axis.

Actuation of the driving member 68 is accomplished by means of a fluid cylinder 74 extending transversely with respect to the axis of rotation of the roll-over frame, and having one end anchored to a bracket 75 carried by the box frame 17. Associated with the cylinder 74 is a power delivery element 76 which is connected to the outer end of the turning bracket 70 by means of a con nection pin 77.

By reference to Fig. 6. it will be observed that the endmost rollers 72 are positioned a greater distance from the center of the tubular member 49 than the rollers at the mid-position of the sector gear. correspondingly, the bottoms of the endmost indentations on the plate 69 are closer to the axis of rotation of the driving member than the intermediate indentations. It is believed that it will therefore be evident that by automatically changing the mechanical advantage so that it is greatest at the plowing positions of the gangs, it is possible to utilize a substantially constant force to actuate the roll-over frame against the greater opposing force due to the offset construction, and thus keep the power means within practical size limits. With the actuating mechanism just described, an added advantage is obtained in that the speed of roll-over is reduced during the periods when the overhang or ofiset forces are in greatest opposition to the power means.

The plowing depth is determined by the cooperative action of the abutment screw 45 and the depth gauging wheel 66. As shown in Figs. 3 and 4 the depth gauging wheel 66 is supported at the outermost end of an arm 78 which is pivotally supported at its innermost end on a bracket 79 secured to the tubular member 49 of the roll-over frame. The pivot support for the arm 78 provides swinging movement of the arm about a pivot member 80 and about a pivot 81, these pivots being in right angle relation. Adjacent the innermost end of the arm 78, a plate 82 is supported on the bracket 79, this plate having a plurality of openings 83 therein for the reception of abutment pins 84 and 85 which are adapted to make engagemnet with a stirrup 86 on the back side of the arm 78.

The number of plowing elements in the plow gangs 17 The outermost ends of the may be reduced in number. For example, when three plowing elements are used in each gang, the caster wheel 16 and its associated party may be eliminated and the roll-over frame supported-upon the tube 50 as a canti-;

rails 30 and 31 are each provided at their pivot end with an angularly extending arm 91 with movements of the tongue. The outer end of this arm is positioned between spaced fixed arms 92 and 93 secured to and angularly projecting fro-m the box frame arms 92 and 93 are provided with aligned openings 94 which are adapted to receive a pin (not shown) which serves as an abutment for the arm 91 when relatively swung in a clockwise direction as viewed in Fig. 2.

During a normal plowing operation, the arm 91 is freely movable between the fixed arms 92 and 93 and is inactive with respect to normal swinging movements of the tongue. At the conclusion of a plowing operation, the raising movement of the carrier frame causes the plow elements to tip upwardly and plow their way out. As the plowing elements move out of the soil, the load on the lifting mechanism is materially reduced, and as raising movemnet of the carrier frame is continued. a point is reached at which the arm 91 strikes the pin in the openings 94. A delayed cantilevering action of the rollover frame now takes place and the rear-end of the rollover frame is raised until the roll-over frame is in a substantially level position for enabling the roll-over operation.

In the plow assembly of Fig. 1, the wheels 11 and 12 cooperate with the caster wheel 16 to form a three point support during transportation of the plow assembly from one location to another. With this form of the invention, the wheel assemblies are latched in raised frame position so as to relieve the power cylinders of load forces during transportation of the equipment. In the case of the wheels 11 and 12, a latching link 96 is pivotally supported on the box frame 17 for swinging movement. The latching link is arranged to be swung into a position, as shown in full lines in Fig. 2 wherein it engages back of the coupler 35 and thus holds the frame in raised position relative to the wheels 11 and 12. The latch, when not used may be moved to an inoperative position.

In the case of the caster wheel 16, a latching link 98 is pivoted at one end on the projecting arm 65' so that its free end may be swung to a position for engagement wtih the end of the fluid cylinder 62 structure, in which position the latching link retains the power delivering element 64 in extended position corresponding with that of the raised position of the adj acent roll-over frame structure. When not in use, the link 98 may be swung to a non-effective position.

Various modifications may suggest themselve to those skilled in the art without departing from the spirit of our invention, and hence, we do not wish to be restricted to the specific form or forms shown or uses mentioned, except to the extent indicated in the appended claims.

We claim:

1. Earth working equipment, comprising: a mobile carrier frame having laterally spaced groutd-contacting wheels; a forwardly extending tongue connected to said frame; a rearwardly extending tool carriage supported on said frame for turning movement about a longitudinal axis to selectively position right-hand and left-hand plow gangs in an operative position, each of said gangs being laterally offset to one side of said longitudinal axis; a fluid cylinder assembly connected to said carrier adapted to swing and power transmitting means between 6 frame and having a movable power delivering element; said element and said tool carriage operative to increase the mechanical advantage of power delivery to said tool carriage at the operative positions of said plow gangs.

Earth working equipment, comprising: a mobile carrier frame having laterally spaced ground-contacting wheels; a forwardly extending tongue connected to said frame; a rearwardly extending tool carriage supported on said frame for turning movement about a longitudinal axis to selectively position right-hand and left hand plow gangs in operative position, each of said gangs being laterally offset to one side of said longitu dinal axis; a power source; and motion transmission means between said source and said tool carriage-having a mechanical advantage variable with the turning movement of said tool carriage so as to provide maximum poweroutputat the operative positions of said plow gangs.

3. Earth working equipment, comprising: a mobile carrier frame having laterally spaced ground-contacting wheels; a forward y extend ng tongue connected to said frame; a rearwardly extending tool carriage supported on said frame for turning movement about a longitudinal axis to selectively move right-hand and left-hand plow gangs between operative positions through an are above. the longitudinal axis, each of said gangs being 'laterallyoffset to one side of said longitudinal axis; a

power source; and variable motion transmission means between said source and said tool carriage for actuating said gangs from one operating position to the other, said transmission means further acting to increase the speed of movement of the power source with respect to the movement of said carriage as the plow gang is moved from substantially mid-arc position to its new operating position.

4. Earth working equipment, comprising: a mobile carrier frame having laterally spaced ground-contacting wheels; a forwardly extending tongue connected to said frame; a rearwardly extending tool carriage supported on said framefor turning movement about a longitudinal axis to selectively position right-hand and lefthand plow gangs in an operative position, each of said gangs being laterally offset to one side of said longitudinal axis; a power source; and motion transmission means having a variable transmission ratio adapted to apply an increased turning movement to said tool carriage in the operative position of each plow gang.

5. Earth working equipment, comprising: a mobile carrier frame having laterally spaced ground-contacting wheels; a forwardly extending tongue connected'to said frame; a rearwardly extending tool carrier supported on said frame for turning movement about a longitudinal axis to selectively move right-hand and left-hand plow gangs between operative positions through an are above the longitudinal axis, each of said gangs being laterally offset to one side of said longitudinal axis; a power source; and variable motion transmission means between said source and said tool carriage for turning said tool carriage to change-said gangs from one operating position to the other, said transmission means and power source cooperating upon passage of the plow gang past mid-roll-over arc position'to cushion the gravitational movement of the plow gang to the new operative position.

6. Earth working equipment, comprising: a mobile carrier frame having laterally spaced ground-contacting Wheels; a forwardly extending tongue connected to said frame; a rearwardly extending tool carrier supported on said frame for turning movement about a longitudinal axis to selectively move right-hand and left-hand plow gangs between operative positions through an are above the longitudinal axis, each of said gangs being laterally offset to one side of said longitudinal axis; a power source and motion transmission means cooperating to actuate the tool carriage and move the plow gang through an initial phase of roll-over, and act as cushioning means in a final phase of roll-over, during which the plow gang exerts a driving turning movement.

7. Earth working equipment, comprising: a mobile carrier frame having laterally spaced ground-contacting wheels; a forwardly extending tongue connected to said frame; a rearwardly extending tool carrier supported on said frame for turning movement about a longitudinal axis to selectively move right-hand and left-hand plow gangs between operative positions through an are above the longitudinal axis, each of said gangs being laterally oifset to one side of said longitudinal axis; a hydraulic cylinder power source including a piston; variable motion transmission means connecting said power source and tool carriage operable in one direction of movement to actuate said gangs from one operating position to the other, and said transmission means further acting to increase the relative movement of said piston and cylinder in said one direction when driven by the plow gang as it moves to a new operating posi tion, whereby the piston and cylinder cooperate to cause an increased retardation effect of the plow gang as it approaches the new operating position.

8. Earth working equipment, comprising: a mobile carrier frame having laterally spaced ground-contacting wheels; at forwardly extending tongue connected to said frame; a rearwardly extending tool carrier supported on said frame for turning movement about a longitudinal axis to selectively move right-hand and left-hand plow gangs between operative positions through an are above the longitudinal axis, each of said gangs being laterally offset to one side of said longitudinal axis; a

power source including a'hydraulic cylinder and associated piston; operating fluid supply and exhaust connections to the cylinder defining a restricted rate of fluid exhaust; variable motion transmission means connecting to drive said pistonagainst fluid pressure in said cylinder depending upon the rate of exhaust from the cylinder.

References Cited in the file of this patent UNITED STATES PATENTS 2,591,711 Moore Apr. 8, 1952 2,807,200 Pursche Sept. 24,1957 FOREIGN PATENTS 1,150 Great Britain of 1872 645,213 Great Britain Oct. 25, 1950 678,376 Great Britain Sept. 3, 1952 UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No, 2 929 456 March 22,: 1960 Roy La Chandler et ,al.

It is hereby certified that error appears in the-printed specification of the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 5, line .3- for ""party" read parts Signed and sealed this 13th day of September 1960,

(SEAL) Attest:

KARL H. AXLINE ROBERT C. WATSON Attesting Officer I Commissioner of Patents 

